DE2828223A1 - ROTARY CONE VALVE - Google Patents

Description

The present invention relates to a rotary cone valve according to the preamble of claim 1. In particular, it relates The present invention relates to such valves in which the closing body rotates about an axis that is perpendicular to extends the axis of the valve seat and is offset from this. The closing body is operated by a valve drive driven, which on the basis of certain values of a control signal a certain position of the closing body and thus causes a certain flow rate of the rotary plug valve.

In known valves of this type, the closing body is carried by a support device, which in turn a shaft is in drive connection. The valve drive rotates the shaft around the aforementioned axis of rotation rotated to bring the closing body in a desired position. This position corresponds to the existing value the control signal, for example a controlling air pressure, which is fed to the valve drive. Here should each such control signal has a corresponding unique position of the closing body and thus a corresponding one Generate the required flow rate of the fluid. A typical example of such a valve is shown in U.S. Patent No. 3,963,211 shown and described, and a typical example of a corresponding valve drive can be found in US Pat. No. 3,985 can be removed.

With regard to the known valves, it has been found in practice that the valve drive is unique Control function in terms of the position of the closing body for positions of the same loses in a so-called unstable control range, which is located between the closed position and the open position of the valve. The location of this unstable area with regard to the closing body movement varies depending on the valve design

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and is usually indicated by the rotational position of the closing body in angular degrees, starting from the closed position.

If the closing body is moved into the unstable area, it can have more than one position at a certain value of the air pressure supplied to the drive. Accordingly, for positions of the closing body in this area, the Closing body position is no longer clearly assigned to the value of the controlling air pressure, so that the closing body position and thus the degree of valve opening can no longer be controlled. This is due to the bistable nature of a torque caused by the flowing fluid on the closing body and exerted on the shaft, this force runs in a so-called critical position of the closing body through a minimum and the minimum in the middle of the unstable area.

Since the control of the closing body position by the drive is not clearly possible in the unstable area it has hitherto been necessary in known valves to restrict the extent of the valve opening so that the closing body does not reach the corresponding unstable area. Usually, however, you want to open every valve that far can ensure that the full flow capacity is achieved.

In the past it has already been proposed to mitigate the aforementioned effect of known valves by that one increases the force of the controlling air pressure counteracting spring of the valve drive. Through this the unstable area of the valve could be shifted somewhat towards a larger valve opening. On the other hand, however, this measure leads to an increased expenditure of force, which the valve drive against the spring force must exercise, whereby the dimensions of the valve drive and its cost are increased.

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It is therefore the object of the present invention to provide a To design rotary cone valve of the type mentioned at the outset in such a way that that it can be regulated in a stable manner over a wide opening range and has a high flow capacity, this being the case Flow capacity not only on the achievable opening position, but also on the structural design of the closing body and its storage is due. The solution to this problem is achieved according to claim 1 marked invention. Further advantageous refinements of the invention can be found in the subclaims.

The rotary cone valve according to the invention has a wing connected to the support device for the closing body on. This wing is arranged and has such a shape that it exerts a rotating force on the shaft of the closing body generated in a flowing fluid. This rotational force acts with the aforementioned generated by the closing body Force together and shifts the unstable area further away from the closed position of the valve, whereby the range of controllable locking body position is expanded. In addition, the wing interferes with the fulfillment of the intended Function the fluid flow only minimally.

Based on one shown in the figures of the accompanying drawings Exemplary embodiment, the invention is described in more detail below. Show it:

Fig. 1, 2 and 3 corresponding views from the front, above and from the side with respect to a preferred embodiment of the present invention, some of which are sectional views acts and the closing body is in its closed position;

Fig. 4 is a partially sectioned view of a

typical pneumatically operated valve drive for moving the closing body of the valve according to FIGS. 1 to 3;

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FIG. 5 shows a side view similar to that according to FIG. 3, but with the closing body in the open position; and

6 shows a series of diagrams to illustrate the operation of the valve in Control by the valve drive shown.

According to FIGS. 1 to 3, the valve has a housing 1 which defines a fluid flow path 3. A seat 5 is fixed inside the housing 1, with its axis in the main coincides with the axis of the fluid flow path 3. The seat is fastened by means of a clamping ring 7. According to FIGS. 1 and 3, the valve seat 5 has a hollow cylindrical shape, one end portion being shaped to form an annular support portion 9, and the opposite end portion is shaped so that it forms a rigid annular seat part Π. The two parts 9 and 11 are Via an annular flexible connection 13 with one another tied together. The clamping ring 7 secures the seat 5 within the housing 1 by the support part 9 against one in the Housing 1 formed shoulder 15 presses.

The closing device 17 of the valve comprises a closing body 19, as well as supporting devices 21 and carrying it. In the same way, the support device 23 comprises a ring part 29 and an HRM 31 which connects the ring part 29 to the closing body 19. The ring part 25 is mounted on a stub shaft 33 and can rotate thereon, the stub shaft 33 being fastened in a bore 35 of the housing 1. An annular disk 37 surrounds the stub shaft 33 and keeps the annular part at a distance from the inner wall of the housing 1.

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The ring part 29 sits on the end of a shaft 39 and is wedged therewith via a wedge 41, which can be seen in FIG. 3 is. The shaft 39 is rotatably mounted in a sleeve 43, the sleeve 43 being inserted into a bore in the housing 1 is used. The shaft 39 rotates about an axis which coincides with the axis of the shaft stub 33 and which is perpendicular is directed to the axis of the valve seat 5 and offset from this.

A wing member 45 is fastened between the support devices 21 and 23. In particular, the wing member 45 comprises a wing part 47 which ends at one end in a connecting part 49 which is fastened to the ring part 25. The opposite end of the wing part 47 ends in a connecting part 51 which is fastened to the ring part 29. As can best be seen from Fig. 3, the wing 47 is arranged within the flow path 3 and has the design a traverse, the longitudinal axis of which extends between the parts 49 and 51 and perpendicular to the axis of the flow path 3. As can also be best seen in FIG. 3, the wing 47 has a cross section in the form of a Oval or a flat diamond with rounded corners.

The valve drive according to FIG. 4 is used to drive the shaft 39 of the valve according to FIGS. 1 to 3 to adjust the position of the closing body 19 to change in accordance with the value of a controlling air pressure supplied to the valve drive. To this end, extend the shaft 39 and the sleeve 43 move from the valve housing 1 into a housing 53 of the valve drive, with part of the housing 1, which surrounds the sleeve 43 and the shaft 39, are connected to the outer wall of the housing 53, as can be seen from FIG.

In addition to the housing 53, the valve drive according to FIG. 4 comprises a membrane housing 55 which contains a membrane 57. The membrane is attached to the upper end of a rod 59, this rod having a slot 61 at the lower end. An end

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a lever 63 engages in the slot 61 and is articulated to the rod 59. The other end of the lever arm 63 is attached to the end of the shaft 39, which extends into the Housing 53 extends. The structure is such that a downward movement of the rod 59 the arm 63 also downward moves and thereby a rotation of the XVeile 39 in the counterclockwise direction when looking from the right of the valve drive to the valve. This direction of observation is hereinafter referred to simply as "towards the valve".

The upper wall of the diaphragm case 55 is screw-connected 65 which is in communication with a fluid chamber between the top wall and the surface of the Membrane 57 is formed. The screw connection 65 is used to connect a. Air line through which the valve drive of the controlling air pressure is supplied. The size of the air pressure determines the position of the closing body and thus the degree of opening of the valve. A spring 67 acts upwards on the ünterflache the membrane 57, the force of which is through the controlling air pressure on the diaphragm is opposite.

The valve shown in FIGS. 1 to 3 is closed by the valve drive 4 when the supplied control air pressure has a certain value. As a result, at a certain maximum value which is sufficient for closing the valve, the membrane 57 is moved against the action of the spring 67 into its lowest position. In this position of the diaphragm 57, the rod 59 and the arm 63 also assume their lowest position and the shaft 39 is viewed in the direction of the valve - rotated as far as possible in the counterclockwise direction. In this rotational position of the shaft 39, the closing body 19 according to FIGS. 1 to 3 assumes a position in which the valve is closed.

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When the controlling air pressure gradually decreases _r so the spring 67 pushes the diaphragm 57 / rod 59 and the arm 63 upwards, whereby the shaft 39 - viewed in the direction of the valve - is rotated clockwise. As a result, the closing body 19 is correspondingly rotated clockwise and moves from its closed position according to FIGS. 1 to 3 into its open position according to FIG Valve opening corresponds to. When the closing body 19 assumes the position shown in FIG. 5, it can be assumed that the components of the valve drive assume the corresponding positions shown in FIG. In this open position of the closing body 19, the transverse dimension of the wing 47 extends essentially along the flow path 3, as can be seen from FIG.

The way in which by the valve construction described above a significantly larger range of controllable closing body positions compared to previously known designs can be achieved will now be described. Reference is made here to the curves according to FIG. 6. In this context it is assumed that the valve is in the usual manner in a fluid-carrying Line is arranged, the fluid flowing against the closing body coming from the seat, as indicated by the arrows according to FIG. 5 is indicated. It is also assumed that a controlling air pressure is supplied to the connection 65 of the drive and that the positions of the closing body 19 and thus the degree of valve opening and the flow through the valve Fluid volume can be specified by the value of this air pressure.

In the following description, let the shaft 39 in the opening direction of the valve or clockwise applied rotational forces simply referred to as opening forces and the opposing forces as closing forces. Furthermore, the mode of operation of the Valve initially described as if the wing member were 45

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not present in the valve, so that the valve turns out to be represents a conventional valve and has the undesirably restricted control range described above. In the following the superior mode of operation of the valve equipped with the wing member 45 will then be described.

Co considered to include in the assumed typical situation the curves of FIG. 6, the dashed curves 69, 71 and 73, the closing body position control obtained in the absence of the wing member 45 illustrate. Fig. 6 also includes the solid curves 75, 77 and 79, which in the presence of the Wing membersK 45 corresponding to curves 69, 71 and 73 Represent target attachments. FIG. 6 also includes a curve 81, which is decisive for valve operation both when the wing member 45 is present and when the wing member 45 is not present.

In particular, the curve 81 shows the relationship between the position of the closing body 19 and the fourth of the by the drive spring 67 opening force exerted. Curves 69 and 75 show the relationship between the position of the closing body 19 and the value of the opening force exerted by the fluid. In the case of the curve 69, this force results solely from the closing body 19, whereas in the case of the curve 75 this force results from the closing body 19 and the wing 47. the Curves 71 and 77 show the resulting opening force that exerted by the spring 67 and the fluid. Finally, curves 73 and 79 show the relationship between posture of the closing body 19 and the closing force generated by the controlling Air pressure is applied across the membrane 57. With regard to curves 69 to 81, the position of the closing body in Degrees of rotation, based on the valve closed position, expressed, as in the description of a valve function is common.

In the absence of a wing member 4 5, it is initially assumed that the closing body 19 is in the position shown in FIGS O ° position is in which the valve is closed

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is. In this closing body position, the closing body 19 lies tightly against the seat part 11 and the fluid is flowed through the D. prevented by the valve. At this time, the spring 67 exerts an opening force with a value indicated by the point 83 of curve 81 is illustrated and the fluid exerts an opening force having a value indicated by point 85 of FIG Curve 69 is illustrated. Both opening forces practice one resulting opening force with a value which is illustrated by the point 87 of the curve 71. The mentioned closed one The position of the closing body 19 is maintained at this point in time by a closing force with a value which is illustrated by the point 89 of the curve 73, this value being the same but opposite of the magnitude Value 87 of curve 71 has «The clamping force values represented by curve 73 correspond to those values represented by the controlling air pressure, which is supplied to the connection 65, can be generated. Frictional forces are neglected here. The closing force curve 73 is therefore a mirror image of the opening force curve 71.

It is now assumed that the controlling air pressure is gradually decreased, whereby the closing force is gradually decreased. Due to the action of the spring 67 and the fluid acting on the closing body 19, the corresponding Forces shown in curves 81 and 69., The position of the closing body is gradually in the opening direction changed, which curve 73 illustrates. As a result, the closing body 19 gradually changes from the initially sealing one System on the seat part 11 moves out, and it forms a gradually increasing fluid flow, which the valve upwards flows through.

According to the curve 69, the opening force or the through the Fluid exerted on the closing body 19 force gradually decreases when the closing body position is continuously in the opening direction is changed. This continues until a closing body position is reached in which the closing body force is through a

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Minimum passes through. This occurs at point 91 on curve 69. Then another movement of the closing body calls a renewed increase in the closing body force in the opening direction emerged. This passage through a minimum value gives the closing body force the aforementioned bistable Characteristic, which is illustrated by the minimum value of curve 69.

The aforementioned bistable characteristic of curve 69 is of course reflected in the resulting curve 71 for the opening force again, in that the curve 71 runs through a corresponding minimum value at a critical point 93. This critical point 93 lies approximately at a 55 ° open position of the valve. It becomes an unstable one here Area formed, which is illustrated by the dashed section 95 under the curves 71 and 73.

As mentioned above, the closing body 19 can in positions assume more than one position in the unstable region 95 for each value of the controlling air pressure, as this is the case Curve 73 represents. Consequently, in the case of closing body positions in the area 95, the closing body position is no longer unambiguous assigned to the value of the controlling air pressure, and control of the closing body position and the degree of opening of the valve is lost. In the example considered Therefore, the controllable range of closing body positions ends at a point 97, that of a closing body position of approximately 47 °, the closing body 19 not being opened beyond this point can be, provided that the control of the closing body position is to be maintained by the drive. The maximum The usable closing body opening in the present example is therefore approximately 47 °. The controllable closing body opening could of course be extended to point 93, which corresponds to a 55 ° division, by a suitable stop to limit the movement of the closing body up to the 55 ° position.

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If the wing member 45 is present, it is again assumed that the closing body is in the 0 ° position in the starting position, in which according to FIGS. 1 to 3, the valve is closed. In this closing body position, the exercise as before Spring 67 from an opening force with a value by point 83 of curve 81 is illustrated. Likewise, the fluid again exerts an opening force with a value which is illustrated by point 85, which two curves 69 and 75 are common. These two opening forces put themselves to a resulting opening force with a Value together, which is again illustrated by the point 87, which is common to the two curves 71 and 77. Again at this point in time the mentioned closed position of the closing body 19 is maintained by a closing force with a value which is illustrated by the point 89, which two curves 73 and 79 are common. As in the case of curves 73 and 71, curve 79 is a mirror image of curve 77.

It is now assumed that the controlling air pressure is gradually reduced, whereby the closing force gradually decreases and the closing body position is gradually changed in the opening direction according to curve 79. As a result, the Closing body 19 again gradually out of its sealing contact with the seat part 11 in the direction of the open position 5 moved out, whereby the fluid flow gradually increases and flows through the valve upwards.

According to curve 75, the opening force generated by the fluid increases again gradually decreases when the closing body position gradually progresses in the opening direction. However, the force generated by the fluid now includes that generated by the wing 47 Opening force, whereby according to the curve 75 this force no longer passes through a minimum in the considered area of the Closing body position runs, but continues to gradually decrease up to the point 99, in which the curve 75 is the zero axis walks through.

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The missing minimum in curve 69 in curve 75 leads to that the curve 77 for the opening force reaches the zero axis at a point 101 without any minimum or a bistable Characteristic would have occurred »As a result, there is no unstable area in terms of opening and closing Closing forces with a controllable closing body position range / which extends up to about 75 °. The maximum usable opening area of the closing body if it is present of the wing 47 therefore exceeds an angle of 70 °. This represents a significant performance improvement in terms of performance to the maximum achievable opening range of 47 ° or 55 °, as it could be achieved with missing wing 47.

It is obvious that the statements made above are also valid when the controlling air pressure is used, to open the valve against the force of the spring. In this case too, the wing 47 enlarges the area with respect to the positions of the closing body in which the drive clearly defines the closing body position. The wing 47 also serves the rotational drive connection of the ring part 25 with the ring part 29, so that the shaft 39 both parts 25 and 29 drives together. The wing 47 accomplishes moreover, this with a minimal disturbance of the fluid flow through the valve, as can be seen in FIGS is. It can be seen that the wing 47 is substantially out of the main flow of the fluid finally to lie in the flow direction according to FIG.

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Claims (7)

Honeywell Plaza 04-4127 Ge Minneapolis, Minn., USA Rotary plug valve Patent claims: Rotary cone valve with a housing through which a fluid flows, a housing arranged symmetrically to the housing axis Valve seat and a closing body that interacts with this and sits on a rotatable shaft, the axis of which is arranged perpendicular to the housing axis and offset to this, whereby the closing body in a rotary movement the shaft experiences a displacement in the direction of the valve seat and away from it by a vane (45, 47) movable in the fluid flow with the closing body (17, 19) for generation a torque acting in the opening direction. 2. Rotary cone valve according to claim 1, characterized that the closing body (17,19) is supported by first and second support devices (21,23) mounted on the shaft (39) and that the wing (45,47) extends between the two support devices (21, 23). 809881/1095 ORIGINAL INSPECTED 3. Rotary cone valve according to claim 2, characterized that the wing by a leaf-shaped traverse (47) with a substantially oval Cross-section is formed. 4. Rotary cone valve according to claim 3, characterized that when the valve is open, the oval cross-section of the cross member (47) is the flowing medium opposes the least resistance. 5. Rotary cone valve according to claim 1, characterized in that the wing (47) is eccentric is arranged to the shaft (39). 6. Rotary cone valve according to claim 5, characterized that the wing (47) is between two radially directed cantilever arms (49,51) extends. 7. rotary cone valve according to claim 2 and claim 6, characterized in that the support means (21,23) the extension arms (49,51) for the wing (47) and support arms (27,31) for the closing body (19), and that the extension arms (49,51) extend substantially at right angles to the support arms (27,31). 809881/1095